Cutting tools for pipe cutting frames

ABSTRACT

Cutting tools for pipe cutting frames are disclosed. Example split frame pipe cutting tools include a frame and a slide tool configured to position a cutting edge in contact with the workpiece, the slide tool comprising: a radial advancement mechanism configured to provide radial advancement of the cutting edge based on circumferential advancement of the slide tool by the frame; and an axial guide rail; a recirculating bearing carriage configured to slide in an axial direction along the axial guide rail and to couple the cutting edge to the axial guide rail; an axial advancement mechanism configured to advance the cutting edge in the axial direction with respect to the workpiece by translating radial advancement by the radial advancement mechanism to axial advancement based on a cutting template coupled to the radial advancement mechanism.

BACKGROUND

This disclosure relates generally to orbital cutting and, moreparticularly, to cutting tools for pipe cutting frames.

A variety of different types of pipe machining apparatuses exist toperform various machining processes on pipes, such as, for example,cutting pipes. One example of such pipe machining apparatuses includes asplit frame pipe machining apparatus, which includes two or more framemembers that surround the pipe from respective sides and couple togetheraround the pipe. Such a pipe cutter includes a tool or cutting devicethat encircles the pipe and moves toward the pipe in small incrementsduring the cutting process in order to slowly cut into the pipe. Thetool is supported by a tool support. Eventually, after many smallincrements of adjustment toward the pipe, the pipe will be completelycut by the tool.

SUMMARY

Cutting tools for pipe cutting frames are disclosed, substantially asillustrated by and described in connection with at least one of thefigures, as set forth more completely in the claims.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a perspective view of one example of a pipe machiningapparatus to support one or more slide tools, in accordance with aspectsof this disclosure.

FIG. 2 is a perspective view of an example implementation of the slidetool of FIG. 1 and a portion of a pipe to be machined with the slidetool.

FIG. 3 is another perspective view of the example slide tool of FIG. 2and the portion of the pipe.

FIG. 4 is a view of a gear mechanism to provide bidirectional radialadvancement for the example slide tool of FIG. 2.

FIGS. 5 and 6 are perspective views of the example gear mechanism ofFIG. 4.

FIG. 7 is a section view of the gear mechanism of FIG. 4.

FIG. 8 is a view of an example implementation of the axial advancementmechanism of the slide tool of FIG. 2.

FIG. 9 is a section view of the axial advancement mechanism of FIG. 2including a section view of the axial advancement mechanism of FIG. 8.

FIG. 10 is a section view of a rail lock and drag assembly including theexample guide rail and the recirculating bearing carriage of FIG. 8.

FIG. 11 is a more detailed section view of the rail lock and dragassembly of FIG. 10.

FIG. 12 is another section view of the example rail lock and dragassembly of FIG. 10.

FIG. 13 is another view of the example axial advancement mechanism.

FIG. 14 is another view of the example cam follower of FIG. 8 a templateholder including a template, the axial advancement mechanism, the raillock and drag assembly, and cutting tool holder with a cutting insert.

FIGS. 15 and 16 are views of an example implementation of the feedactuation component of FIG. 2.

FIGS. 17 and 18 are views of the example feed component of FIG. 2.

FIG. 19 is a section view of the example feed component of FIGS. 2 and17.

The figures are not necessarily to scale. Similar or identical referencenumerals may be used to refer to similar or identical components.

DETAILED DESCRIPTION

As used herein, the terms “axial” and “radial” are used with referenceto a pipe or other workpiece being worked upon by disclosed examples.For example, references to an axial direction mean in the axialdirection of the pipe or other workpiece (e.g., along the axis of thepipe or other workpiece). Similarly, references to a radial directionmean the radial direction of the pipe or other workpiece (e.g., towardor away from the axis of the pipe or other workpiece).

With reference to FIG. 1, one example of a pipe machining apparatus 20adapted to machine pipes of varying diameters is illustrated. Thisexample of a pipe machining apparatus 20 is configured to include thetool support 48 shown in FIGS. 2 and 3. In some exemplary embodiments,the apparatus 20 completely cuts through pipes 22. In other exemplaryembodiments, the apparatus 20 prepares an end of a pipe for coupling toanother pipe. In still other exemplary embodiments, the apparatus 20both completely cuts and prepares a pipe for coupling to another pipe.The illustrated example of a pipe machining apparatus 20 is only onetype of a wide variety of pipe machining apparatuses that may employ thefeatures of the present disclosure and the illustrated example is notintended to limit the present disclosure in any manner.

In the illustrated example, pipe machining apparatus 20 is formed offour joined-together sections 24A, 24B, 24C, 24D and includes a frame 28and a tool carrier 32. The four joined together sections 24A, 24B, 24C,24D encircle the pipe 22 and together comprise the frame 28 and the toolcarrier 32. A drive mechanism 34 is coupled to a periphery 35 of theframe 28. In the illustrated example, the drive mechanism 34 includes apair of drive motors 44A, 44B such as, for example, an air and/orhydraulic motor with suitable gear reduction means. In other examples,the drive mechanism 34 may be comprised of other quantities of motors orother types of drive mechanisms. The frame 28 is adapted to couple andbe fixed relative to a pipe, and the tool carrier 32 is rotatablerelative to the fixed frame 28 and the pipe. The drive mechanism 34 isadapted to rotate the tool carrier 32 relative to the frame 28 through agear train. In this example manner, the tool carrier 32 providescircumferential advancement to one or more cutting tools around the pipe22.

The rotatable tool carrier 32 includes one or more tool supports 48 (twotool supports 48 shown in the illustrated example), which support tools52 for performing a cutting or machining operation on the pipe as thetools 52 rotate circumferentially about the pipe 22. Both tool supports48 illustrated in FIG. 1 are the same type of tool support and are oneexample of many different types of tool supports of the presentdisclosure. The tool support 48 illustrated in FIGS. 2 and 3 ismountable to the pipe machining apparatus 20 in a similar location andin a similar manner to the example illustrated in FIG. 1. The toolsupports 48 are coupled to the tool carrier 32 by a plurality offasteners 16. The machining operation performed by the tool(s) 52 mayform a straight edge substantially perpendicular to a longitudinalextent of the pipe 22, a bevel on an end of the pipe 22 that istransverse to and at an angle other than ninety-degrees to thelongitudinal extent of the pipe 22, or an edge of a pipe 22 having anyangle. Such a bevel may be formed on either an inner surface of the pipe22 or an outer surface of the pipe 22.

The apparatus 20 further includes a plurality of coupling members 68engageable with an exterior of the pipe 22 and having suitableadjustability to couple and concentrically or axially locate theapparatus 20 to the exterior of the pipe 22. The coupling members 68 arealso positionable on the apparatus 20 to engage an interior of the pipe22 and are suitably adjustable to couple and concentrically or axiallylocate the apparatus 20 to the interior of the pipe 22.

Tool carrier 32 is rotatably mounted on and supported by frame 28 by aplurality of roller bearings positioned between the frame 28 and thetool carrier 32. The roller bearings ride in a circular bearing race onthe interior of tool carrier 32.

The apparatus 20 also includes a bidirectional radial advancementmechanism 80 that is adjustable into and out of a path of an advancementmember 84 coupled to each tool support 48 to advance the tool 52 towardthe pipe 22.

FIG. 2 is a perspective view of an example implementation of the slidetool 100 of FIG. 1 and a portion of a pipe 102 to be machined with theslide tool 100. FIG. 3 is another perspective view of the example slidetool 100 and the portion of the pipe 102. In contrast with conventionalslide tools, the example slide tool 100 is configurable to perform pipefacing, outer diameter surfacing, inner diameter surfacing, and/orcutting or boring of the pipe 102 by different configurations of theslide tool 100 and/or the use of different cutting tips. The apparatus20 may support one or more of the slide tools 100, where additionalslide tools increase the speed of processing the pipe 102.

The slide tool 100 may be supported on the tool support 48 of FIG. 1 toposition a cutting tip 108 having a cutting edge in contact with aworkpiece (e.g., the pipe 22) to perform cutting or boring on theworkpiece for radial movement of a cutting tip 108. The example slidetool 100 is capable of bidirectional radial tracking and bidirectionalaxial tracking. The slide tool 100 may form cuts having differentprofiles using one or more templates 104. The example slide tool 100improves on conventional tools in that the slide tool 100: 1) is modularand can be mounted on slide base for multiple machining platforms; 2) islighter weight; 3) has a capability for automatic axial feeding inaddition to automatic radial feeding; 4) has a capability to reversefeed directions in both axial feeding and radial feeding; 5) has aspring-loaded drag system that offers superior performance overconventional cutting tools, and 6) increases cutting speeds byincreasing the cut depth. In some examples, the slide tool 100 has axialand/or radial cutting ranges that enable the cutting tip 108 to performcutting all the way to the clamping feet of the frame 28 that hold theframe 28 onto the pipe 102. These and other advantages will be describedin more detail below.

The example slide tool 100 includes an automatic radial advancementmechanism 106 to provide bidirectional radial advancement of the cuttingtip 108 based on circumferential advancement of the slide tool 100(e.g., by the tool carrier 32). The example slide tool 100 also includesan axial advancement mechanism 110 to provide bidirectional axialadvancement of the cutting tip 108. The radial advancement mechanism 106is triggered to feed the cutting tip 108 in the radial direction byinteraction between the radial advancement mechanism 106 and one or moreadvancement points around the circumference of the frame 28. Similarly,the axial advancement mechanism 110 may be triggered by an axial feedmechanism 116 to feed the cutting tip 108 in the axial direction byinteraction between the axial advancement mechanism 110 and the one ormore advancement points around the circumference of the frame 28 and/ormay advance the cutting tip 108 in the axial direction with respect tothe workpiece by translating radial advancement by the radialadvancement mechanism 106 to axial advancement based on the cuttingtemplate 104 coupled to the radial advancement mechanism 106.

The example axial feed mechanism 116, discussed in more detail below,advances the axial advancement mechanism 106 based on thecircumferential advancement of the slide tool 100 by the tool carrier32. The axial feed mechanism 116 may be enabled or disabled based on thedesired cutting operation (e.g., disabled when the template 104 isused).

The example slide tool 100 includes a cam follower 112 coupled to theaxial advancement mechanism 110 that causes axial movement in thecutting tip 108 in response to radial movement of the cutting tip by theradial advancement mechanism 106. The axial movement in the cutting tip108 relative to the radial movement caused by the radial advancementmechanism 106 is determined using the template 104. The template 104 maycause the cutting tip 108 to machine, into the workpiece, a straightedge substantially perpendicular to a longitudinal extent of theworkpiece. The template 104 may alternatively cause the cutting tip 108to machine a bevel on an inner surface of an end of the workpiece thatis transverse to and at one or more angles other than ninety-degrees, tothe longitudinal extent of the workpiece, and/or machine a bevel on anouter surface of the end of the workpiece that is transverse to and atone or more angles, other than ninety-degrees, to the longitudinalextent of the workpiece. In still other examples, the template 104 maycause the cutting tip 108 to machine an edge having one or more anglesinto the workpiece. Different templates may be used and/or configured toachieve the desired operation. Additionally or alternatively, the radialadvancement mechanism 106 may be locked to perform boring into the pipe102 (e.g., only in the axial direction).

The example slide tool 100 has sufficiently high rigidity under load sothat pressure between the cam follower 112 and the template 104 does notcause the cam follower 112 to be locked against the template 104 duringcutting operations. For example, the high torque loads on the axialadvancement mechanism 110 during cutting operations could, withoutsufficient stiffness and lubricity in the axial advancement mechanism110, cause the cam follower 112 to be loaded against the template 104 tosuch a degree that axial movement would be prevented and/or the slidetool 100 could be damaged.

FIG. 4 is a view of a gear mechanism 400 to provide bidirectional radialadvancement for the example slide tool of FIG. 2. FIGS. 5 and 6 areperspective views of the example gear mechanism 400 of FIG. 4. FIG. 7 isa section view of the gear mechanism 400 of FIG. 4. As illustrated inFIGS. 1 and 7, a slide base 114 is mounted to the radial slide 410.

The gear mechanism 400 is an implementation of the radial advancementmechanism 106. The gear mechanism 400 includes a stationary gear 402 andswappable gears 404, 406. The swappable gear 406 is coupled to a starwheel gear 408 that contacts and rotates in response to interfacing withthe advancement points around the circumference of the frame 28. Whenthe star wheel gear 408 contacts an advancement point, the star wheelgear 408 is rotated a fixed amount, thereby rotating the swappable gear406 with the same angular rotation.

The stationary gear 402 is coupled to a radial slide 410 via a feedscrew 412. A track 418 mounted to and/or integral to the frame 28contains movement of the radial slide 410 to the radial direction, whilethe advancement of the radial slide 410 is controlled by turning thefeed screw 412 and, thus, by turning the stationary gear 402.

The rotation of the swappable gear 406 rotates the stationary gear 402in either direction, depending on which of two slots 414, 416 theswappable gear 406 is installed, to enable bidirectional automaticradial feeding. If the swappable gear 406 is installed in the slot 414,the swappable gear 406 has a direct coupling (e.g., direct contact) withthe stationary gear 402, and rotation of the swappable gear 406 in theslot 414 rotates the stationary gear 402 in a first direction andadvances the radial slide 410 in a first direction. Conversely, when theswappable gear 406 is installed in the slot 416, the swappable gear 406is coupled to the stationary gear 402 via the swappable gear 404 and isin contact with to the stationary gear 402, which results in reversingthe direction of rotation of the stationary gear 402 when the swappablegear 406 is turned in the same direction. Thus, the feed screw 412 isturned in a first direction to radially feed the radial slide 410 in afirst radial direction when the swappable gears 406 are in a firstconfiguration with respect to the slots 414, 416, and the feed screw 412is turned in a second direction to radially feed the radial slide 410 ina second radial direction (e.g., opposite the first radial direction)when the swappable gears 406 are in a second configuration (e.g.,opposite the first configuration) with respect to the slots 414, 416.

FIG. 8 is a view of an example implementation of the axial advancementmechanism 110 of the slide tool 100 of FIG. 2. FIG. 9 is a section viewof the axial advancement mechanism 110 of FIG. 8 including a sectionview of the axial advancement mechanism 110. The axial advancementmechanism 110 is configured to hold the cutting tip 108 and to feed thecutting tip 108 in the axial direction via an outer axial slide 802 andan inner axial slide 804. While the example outer axial slide 802 has arectangular cross section, in other examples the outer axial slide 802is cylindrical or another appropriate shape. As shown in FIGS. 8 and 9,the axial advancement mechanism 110 includes a slide tensioning block808, a slide tensioning handle 810, a cam follower 812, a cam bearingblock 814, a tool holder retaining plate 816, a feed screw 818, a toolholder nut 820, tensioning nuts 822, a guide rail 824, a recirculatingbearing carriage 826, and a slide block 828.

The cam bearing block 814 includes a bearing for the cam follower 812.The cam follower 812 is coupled to the guide rail 824 and the outeraxial slide 802. The cam follower 812 translates radial advancement bythe radial advancement mechanism 106 to axial advancement of the outeraxial slide 802 based on a shape of the template 104. To slide in theaxial direction, the outer axial slide 802 is coupled to the guide rail824. The recirculating bearing carriage 826 slides along the guide rail824. The slide block 828 attaches the recirculating bearing carriage 826to the slide base 114.

FIG. 10 is a section view of a rail lock and drag assembly 1000including the example guide rail 824 and the recirculating bearingcarriage 826 of FIG. 9. FIG. 11 is a more detailed section view of therail lock and drag assembly 1000 of FIG. 10. FIG. 12 is another sectionview of the example rail lock and drag assembly 1000 of FIG. 10.

As illustrated in FIG. 9, the recirculating bearing carriage 826includes recirculating bearings to permit the recirculating bearingcarriage 826 to slide along the guide rail 824. Example recirculatingbearings include ball bearings and/or needle bearings (or othercylindrical bearings). The recirculating bearing carriage is capable ofsliding along the guide rail 824 even under substantial torque that maybe applied to the recirculating bearing carriage 826 during operation.While an example guide rail 824 is illustrated in FIGS. 9-12, otherexample guide rail profiles may be used that permit the use ofrecirculating bearing carriages may be used. For example, the guide railmay be cylindrical. The example rail lock and drag assembly 1000includes the slide tensioning block 808, the slide tensioning handle810, and tensioning blocks 1002, 1004. Example tensioning blocks 1002,1004 are constructed using a bronze alloy to provide both high strengthand high lubricity to enable sliding along the guide rail 824 under acutting load (e.g., without locking). The slide tensioning block 808includes one or more disc springs 1006 that cause the tensioning blocks1002, 1004 to apply at least a threshold compression to the guide rail824. Thus, the tensioning blocks 1002, 1004, the recirculating bearingcarriage 826, and the guide rail 824 provide sufficient rigidity whenusing the cam follower 812 and the template 104 that the torque load onthe outer axial slide 802 does not lock the cam follower 812 against thetemplate 104. The rigidity permits the cam follower 812 to move freelywithin the template 104 in response to radial travel of the slide tool100.

Additionally or alternatively, the slide tensioning block 808 may belocked against the guide rail 824 to configure the axial advancementmechanism 110 to advance the cutting tip 108 in the axial direction withrespect to the workpiece via advancing the axial feed mechanism 116. Theslide tensioning handle 810 may be tightened to lock the tensioningblocks 1002, 1004 against the guide rail 824 (e.g., to apply asufficiently high compressive load to prevent movement between therecirculating bearing carriage 826 and the guide rail 824), to therebylock the outer axial slide 802 against axial movement. Locking the slidetensioning handle 810 may be used to perform boring, cutting, and/orfacing without the template 104.

FIG. 13 is another view of the example axial advancement mechanism 110of FIG. 8. FIG. 14 is another view of the example cam follower of FIG. 8and a template holder including a template. The example outer axialslide 802 may include markings 1302, 1304 to illustrate the range ofaxial travel of the outer axial slide 802. While a first distancebetween the markings 1302, 1304 is illustrated in FIG. 13, the exampletemplate 104, the cam follower 812, and the outer axial slide 802 may beadjusted to reset the outer axial slide 802 for further axial travel ofthe cutting tip 108 beyond the nominal axial range indicated by themarkings 1302, 1304.

FIG. 14 also shows the cutting tip 108 installed in a cutting tip holder1402, which is attached to the inner axial slide 804 by a bolt 1404 orother fastener.

Returning to FIGS. 2, 8, and 9, the inner axial slide 804 is advancedvia the axial feed mechanism 116. The example axial feed mechanism 116is used to axially feed the cutting tip 108 instead of using thetemplate 104. The example axial feed mechanism 116 includes a feedcomponent 118 and a feed actuation component 120. A feed cable 122couples the feed component 118 to the feed actuation component 120 toperform actuation of the feed component 118. The feed actuationcomponent 120 actuates the feed component 118 via the feed cable 122 byinteraction between the feed actuation component 120 and one or moreadvancement points around the circumference of the frame 28, similar tothe radial advancement mechanism 106. Actuation of the feed component118 feeds the axial advancement mechanism 110. As described in moredetail below, the direction of axial feeding may be configured byconfiguring the feed component 118.

FIGS. 15 and 16 are views of an example implementation of the feedactuation component 120. The feed actuation component 120 includes a campivot arm 1502 configured to contact a stationary contact surface 1504on the frame 28. The cam pivot arm 1502 is coupled to a spring-loadedcable pull 1506, which is coupled to the feed cable 122. The motion ofthe cam pivot arm 1502 over the stationary contact surface 1504 causesthe cam pivot arm 1502 to pull the feed cable 122 via the spring-loadedcable pull 1506. A feed nut 1508 controls an inner cable position of thefeed cable 122 relative to an outer cable sheath of the feed cable 122,which increases or decreases the length of inner cable between the campivot arm 1502 and the cam follower. When the feed nut 1508 is rotated,the start position of the cam follower to the cam is adjusted, whichincreases or decreases the feed stroke by the cam pivot arm 1502 at eachinteraction with the stationary contact surface 1504.

The cam pivot arm 1502 includes a contact end 1510 and a cable end 1512.The contact end 1510 is configured to contact and slide or roll over thestationary contact surface 1504. The cable end 1512 is coupled to thecontact end 1510 by a pivot point 1514 such that the movement of thecontact end 1510 causes corresponding movement of the cable end 1512,thereby pulling on the feed cable 122. In the example of FIGS. 15 and16, as the cam pivot arm 1502 moves in the circumferential direction,the cam pivot arm 1502 contacts and the stationary contact surface 1504.The cam pivot arm 1502 rotates to travel over the stationary contactsurface 1504, causing the cam pivot arm 1502 to rotate and, thus, pullon the cable end 1512 to pull on the feed cable 122. Differentimplementations of the cam pivot arm 1502 and stationary contact surface1504 may be used.

As illustrated in FIG. 16, the stationary contact surface 1504 may belocated proximate to the advancement points for the star wheel gear 408.Thus, the radial advancement mechanism 106 and the feed actuationcomponent 120 may be located at substantially the same location(s) onthe circumference of the frame 28.

FIGS. 17 and 18 are views of the example feed component 118. FIG. 19 isa section view of the example feed component 118. The feed component118, when actuated by the feed cable 122, feeds the inner axial slide804 by an incremental length, which may be adjusted via the feedactuation component 120. The feed component 118 can be configured tofeed in either axial direction.

The example feed component 118 includes a feed top plate 1702, a radialfeed clutch lever 1704, a radial feed lever bushing 1706, an axial feedscrew 1708, a radial feed coupler ring 1710, a retractable pin 1712, aquick release pin 1714, a hand wheel 1716, a roller clutch bearing 1718,a needle thrust bearing 1720, a thrust washer bearing 1722, a clutch nut1724, and a tensioning nut 1726.

The feed top plate 1702 includes an anchor slot 1728 into which ananchor tab 126 of the feed cable 122 is inserted to anchor the feedcable 122 to the feed top plate 1702. The quick release pin 1714 couplesthe feed cable 122 to the radial feed clutch lever 1704. The feedactuation component 120 pulls on the feed cable 122, and the anchor tab126 and the anchor slot 1728 enable the feed cable 122 to exert apulling force on the radial feed clutch lever 1704 relative to the feedtop plate 1702.

The roller clutch bearing 1718 provides one-directional rotation andresists rotation in the opposite direction. The retractable pin 1712engages the radial feed clutch lever 1704 to the roller clutch bearing1718 via the radial feed coupler ring 1710. The retractable pin 1712 maybe disengaged from the radial feed coupler ring 1710 to enablebidirectional adjustment of the axial feed screw 1708 via the hand wheel1716.

The radial feed clutch lever 1704 includes two slots 1730, 1732 to whichthe feed cable 122 can be coupled via the quick release pin 1714. Thefirst slot 1730 causes the feed cable 122 to advance the axial feedscrew 1708 (and the inner axial slide 804 to which the axial feed screw1708 is coupled) in a first feed direction. The second slot 1732 causesthe feed cable 122 to advance the axial feed screw 1708 (and the inneraxial slide 804) in a second direction. In addition to connecting thefeed cable 122 to one of the two slots 1730, 1732 to configure the feeddirection, changing the axial feed direction of the feed component 118further includes accessing and flipping the direction of the rollerclutch bearing 1718. For example, the hand wheel 1716, the clutch nut1724, and the radial feed lever bushing 1706 are removable to access theroller clutch bearing 1718.

In some disclosed examples, all of the nuts have a same head size toenable manipulation of the nuts in the examples using a single wrenchsize. However, different nut head sizes may be used in other examples.

As utilized herein, “and/or” means any one or more of the items in thelist joined by “and/or”. As an example, “x and/or y” means any elementof the three-element set {(x), (y), (x, y)}. In other words, “x and/ory” means “one or both of x and y”. As another example, “x, y, and/or z”means any element of the seven-element set {(x), (y), (z), (x, y), (x,z), (y, z), (x, y, z) }. In other words, “x, y and/or z” means “one ormore of x, y and z”. As utilized herein, the term “exemplary” meansserving as a non-limiting example, instance, or illustration. Asutilized herein, the terms “e.g.,” and “for example” set off lists ofone or more non-limiting examples, instances, or illustrations. Asutilized herein, circuitry is “operable” to perform a function wheneverthe circuitry comprises the necessary hardware and code (if any isnecessary) to perform the function, regardless of whether performance ofthe function is disabled or not enabled (e.g., by a user-configurablesetting, factory trim, etc.).

While the present method and/or system has been described with referenceto certain implementations, it will be understood by those skilled inthe art that various changes may be made and equivalents may besubstituted without departing from the scope of the present methodand/or system. In addition, many modifications may be made to adapt aparticular situation or material to the teachings of the presentdisclosure without departing from its scope. For example, block and/orcomponents of disclosed examples may be combined, divided, re-arranged,and/or otherwise modified. Therefore, the present method and/or systemare not limited to the particular implementations disclosed. Instead,the present method and/or system will include all implementationsfalling within the scope of the appended claims, both literally andunder the doctrine of equivalents.

What is claimed is:
 1. A split frame pipe cutting tool, comprising: atool carrier comprising a plurality of sections, configured to encirclea workpiece when the sections are connected, and configured to providecircumferential advancement around the workpiece; and a slide toolconfigured to position a cutting edge in contact with the workpiece, theslide tool comprising: a radial advancement mechanism configured toprovide radial advancement of the cutting edge based on circumferentialadvancement of the slide tool by the tool carrier; and an axial guiderail; a recirculating bearing carriage configured to slide in an axialdirection along the axial guide rail and to couple the cutting edge tothe axial guide rail; an axial advancement mechanism configured toadvance the cutting edge in the axial direction with respect to theworkpiece by translating radial advancement by the radial advancementmechanism to axial advancement based on a cutting template coupled tothe radial advancement mechanism.
 2. The split frame pipe cutting toolas defined in claim 1, wherein the template is configured to cause thecutting edge to machine, into the workpiece, a straight edgesubstantially perpendicular to a longitudinal extent of the workpiece.3. The split frame pipe cutting tool as defined in claim 1, wherein thetemplate is configured to cause the cutting edge to machine at least oneof the following into the workpiece: a bevel on an inner surface of anend of the workpiece that is transverse to and at one or more anglesother than ninety-degrees, to the longitudinal extent of the workpiece;or a bevel on an outer surface of the end of the workpiece that istransverse to and at one or more angles, other than ninety-degrees, tothe longitudinal extent of the workpiece.
 4. The split frame pipecutting tool as defined in claim 1, wherein the template is configuredto cause the cutting edge to machine an edge into the workpiece, theedge having one or more angles.
 5. The split frame pipe cutting tool asdefined in claim 1, further comprising a slide tensioning blockconfigured to be selectively locked against the axial guide railwherein, when the slide tensioning block is locked against an axialguide rail, the axial advancement mechanism is configured to advance thecutting edge in the axial direction with respect to the workpiece byadvancing an axial feed mechanism configured to advance the axialadvancement mechanism based on the circumferential advancement of theslide tool by the tool carrier.
 6. The split frame pipe cutting tool asdefined in claim 5, wherein the recirculating bearing carriage iscoupled to the axial guide rail with sufficient strength, rigidity, andlubricity to enable the recirculating bearing carriage to slide alongthe axial guide rail under a cutting load.
 7. The split frame pipecutting tool as defined in claim 5, wherein the axial advancementmechanism comprises a cam follower coupled to the axial guide rail andconfigured to translate the radial advancement to the axial advancementbased on a shape of the template, the recirculating bearing carriage iscoupled to the axial guide rail with sufficient strength, rigidity, andlubricity to enable the recirculating bearing carriage to withstand atorque load from cutting without locking.
 8. The split frame pipecutting tool as defined in claim 1, wherein the axial advancementmechanism comprises a cam follower coupled to the axial guide rail andconfigured to translate the radial advancement to the axial advancementbased on a shape of the template.
 9. The split frame pipe cutting toolas defined in claim 1, wherein the radial advancement mechanismcomprises a star wheel coupled to a screw, the screw configured toadvance the cutting edge in a radial direction proportional to rotationof the screw, the star wheel positioned to contact a stationarycomponent of the tool carrier which, when contacted by the star wheel,causes rotation of the star wheel and rotation of the screw by the starwheel.
 10. The split frame pipe cutting tool as defined in claim 9,wherein the star wheel is positionable in one of two slots such that:positioning of the star wheel in a first one of the slot causes rotationof the star wheel to rotate the screw in a first direction to advancethe cutting edge in a first radial direction; and positioning of thestar wheel in a second one of the slot causes rotation of the star wheelto rotate the screw in a second direction via an intermediate gear, toadvance the cutting edge in a second radial direction opposite the firstradial direction.
 11. The split frame pipe cutting tool as defined inclaim 1, wherein the axial guide rail comprises a bronze alloy.
 12. Thesplit frame pipe cutting tool as defined in claim 1, wherein the slidetensioning block comprises one or more disc springs configured to applyat least a threshold compression between the slide tensioning block andthe axial guide rail.
 13. The split frame pipe cutting tool as definedin claim 1, wherein the axial feed mechanism comprises: a roller clutchbearing configured to rotate an axial screw in a first direction andconfigured to resist rotation in a second direction opposite the firstdirection; and a feed cable configured to actuate the roller clutch inthe first direction in response to tensioning of the feed cable; and apivot arm configured to apply tension to the feed cable in response toactuation of the pivot arm caused by the pivot arm contacting astationary component of the tool carrier.
 14. The split frame pipecutting tool as defined in claim 13, wherein the feed cable isconfigured to be decoupled from the roller clutch bearing when the axialadvancement mechanism is translating radial advancement by the radialadvancement mechanism to axial advancement based on a cutting template.15. The split frame pipe cutting tool as defined in claim 14, furthercomprising a feed nut configured to increase or decrease a feed strokeof the pivot arm on the feed cable.
 16. The split frame pipe cuttingtool as defined in claim 14, wherein the roller clutch is reversible.17. The split frame pipe cutting tool as defined in claim 14, furthercomprising: a plunger and a radial feed coupler ring configured tocouple the roller clutch bearing to the feed cable; and a hand wheelconfigured to enable bidirectional manual adjustment of the axial screwwhen the plunger is disengaged from the radial feed coupler ring. 18.The split frame pipe cutting tool as defined in claim 17, furthercomprising a radial feed clutch lever configured to couple the feedcable to the roller clutch bearing and to translate tension from thefeed cable to rotation of the roller clutch bearing.
 19. The split framepipe cutting tool as defined in claim 1, further comprising a secondslide tool configured to position a second cutting edge in contact withthe workpiece to performing cutting or boring on the workpiece, thesecond slide tool being positioned at a second position on the toolcarrier.
 20. A split frame pipe cutting tool, comprising: a tool carriercomprising a plurality of sections, configured to encircle a workpiecewhen the sections are connected, and configured to providecircumferential advancement around the workpiece; a plurality of slidetools configured to position a plurality of cutting edges in contactwith the workpiece, each of the slide tools comprising: a radialadvancement mechanism configured to provide radial advancement of thecutting edge based on circumferential advancement of the slide tool bythe tool carrier; an axial advancement mechanism configured to: hold thecutting edge; and advance the cutting edge in an axial direction withrespect to the workpiece by: when a slide tensioning block is lockedagainst an axial guide rail, advancing an axial feed mechanismconfigured to advance the axial advancement mechanism based on thecircumferential advancement of the slide tool by the tool carrier; andwhen the slide tensioning block is not locked against the axial guiderail, translating radial advancement by the radial advancement mechanismto axial advancement based on a cutting template coupled to the radialadvancement mechanism.